Rotary device



March 11, 1969 v, D ED 3,4-.' $1,894

ROT ARY DEVI CE Filed March 8, 1967 Sheet of 4 1 N VEN TOR.

Y yozzflxijZf'ed March 11, 1969 v. 0. ALLRED 3,431,394

ROTARY DEVICE Filed March a, 1967 Sheet 3 of 4 I N VEN TOR.

V. D. ALLRED ROTARY DEVICE March 11, 1969 Sheet F'ned March 8 1967 March 11, 1969 v. D. ALLRED 3,431,894

ROTARY DEVICE Filed March a. 1967 Sheet 4 of 4 I N VEN TOR.

Wax/L51 zjZred K/ ATTORNEYS United States Patent 3,431,894 ROTARY DEVICE Von D. Allred, Box 24, Afton, Wyo. 83110 Filed Mar. 8, 1967, Ser. No. 621,629 US. Cl. 1238 16 Claims Int. Cl. F02b 57/04; F04b 29/00 ABSTRACT OF THE DISCLOSURE A rotary device which may be utilized as an internal combustion engine, a compressor, a fluid motor or the like has a spherical rotor which has outwardly extending shafts on the axis of its rotation and has a passageway defining a cylinder in which pistons are mounted. The rotor is mounted for rotation about the shafts in a housing which has a complementary spherical cavity and means including an inlet and outlet port for applying and removing a pressurized fluid to the cavity. The pistons are connected to a crank arm which is disposed in the cylinder and is adjustably secured to the housing so that the timing of the stroke of the piston can be adjusted relative to the angular position of the cylinder with respect to the inlet and outlet ports of the housing. The rotary device includes an embodiment in which an ignition means is included to produce an internal combustion engine and a second embodiment in which the inlet and outlet means are adjacent each other and opposite the ignition means to form a two-cycle internal combustion engine.

BACKGROUND OF THE INVENTION Field 0 the invention The field of art to which this invention pertains is a fluid actuated rotary motor and in particular an internal combustion rotary engine.

Descripti n of the prior art Rotary devices such as rotary combustion engines are well known in the prior art. These engines usually comprise a group of cylinders mounted for rotation around a fixed or stationary crank. Disposed in the cylinders are pistons which are mounted or attached for rotation about the crank. The rotary engine operates by a gas forcing the pistons away from the top of the cylinder to cause the piston and its cylinder to revolve about the fixed crank. The energy developed by the engine is transferred by a drive means attached to the rotating cylinders.

A second type of rotary engine of the prior art comprises :a housing which may have a spherical cavity. Disposed in the housing on a crank is a nutator which coacts with a rotator. As the nutator and rotator revolve about an axis, the working surfaces of the nutator and rotator will move with respect to each other to vary the volume defined by these surfaces. The device is operated by a fluid pressure acting on the two working faces which cause the rotator and nutator to increase the volume between the working surfaces and, therefore, cause the nutator to revolve about its axis and transmit movement to the crank.

Summary of the invention The present invention utilizes a housing having a spherical cavity and a spherical rotor that has a cylinder with pistons positioned therein mounted in this cavity. The pistons are attached to a fixed crank so that when the pressure on the working face of the piston is applied, the rotor and pistons will orbit about the fixed crank and deliver a rotational force through a shaft attached to the rotor.

Accordingly, it is an object of the present invention to provide a novel rotary device in which the rotating parts have a minimum amount of inertia.

A still further object of the invention is to provide a novel four-cycle internal combustion rotary device in which the pistons orbit around the crank and have a minimum inertia to be counteracted.

Another object of the invention is a rotary device in which the rotor is spherical and may be easily sealed within the rotor housing.

A still further object of the invention is to provide a novel fluid motor in which the pistons orbit about a fixed crank and have a minimum inertia that must be overcome at the end of each stroke.

Another object of the invention is to provide a novel two-cycle rotary engine in which the pistons of the engine orbit about a fixed crank and have a minimum inertia to overcome at the end of each stroke.

Yet another object of the invention is to provide a rotary device in which the cylinder is bored through a perfect sphere and is easily sealed with the housing cavity by expansion rings.

Brief descriptiwt of the drawings FIG. 1 is a cross-sectional view with some parts in elevation for a four-cycle internal combustion rotary engine;

FIG. 2 is a cross-section taken on lines IIII of FIG 1;

FIG. 3 is a view taken on section line IIIIII of FIG. 1;

FIG. 4 is a cross-sectional view with some parts in elevation and with some parts out of alignment for purposes of illustration of a two-cycle rotary internal combustion engine;

FIG. 5 is a cross-section taken on line V-V of FIG. 4; and

FIG. 6 is a cross-sectional view with some parts in elevation of a fluid motor.

As shown on the drawings:

The principles of this invention are particularly useful when embodied in a rotary device such as the fourcycle internal combustion rotary engine illustrated in FIG. 1 and generally indicated by the numeral 10.

The engine 10 has as its primary parts a housing means generally indicated by the numeral 11, a rotor 12, pistons 13, 13' a crank means 14 and a control means generally indicated by the numeral 15.

The housing means 11 is made-up of a plurality of portions such as 16 and 17 which are joined together by fastening means such as bolts 18. The housing means 11 has an inner surface 19 which defines a cavity 20. The inner surface 19 may be a surface of revolution about an axis and preferably is substantially spherical. The housing means 11 has a cylindrical passageway 21 extending along the axis of revolution and concentric therewith. The cylindrical passageway 21, as illustrated in FIG. 1, extends from the external surface of the housing means 11 through the center of the cavity to the opposite external surface of the housing means. The cylindrical passageway 21 has enlarged portions 22 and 23 adjacent to the cavity 20. The housing means 11 has an inlet means 24 and an outlet or exhaust means 25 provided therein.

The rotor 12 has a surface 26 which is a surface of revolution about the rotors axis of rotation. Surface 26 conforms with the inner surface 19 of the housing means and is therefore preferably spherical. The rotor 12 has a shaft 27 with an axis that coincides with the axis of rotation. The rotor, as illustrated in FIG. 1, is disposed in the housing with the shaft 27 extending through the bore 21. The shaft 27 is rotatably supported in the bore 21 by means of a bearing such as the ball bearing 28 that is positioned in the enlarged portion 22. The rotor 12 has a cylindrical extension 29 which is concentric with the axis of rotation. The extension 29 extends in the opposite direction from the shaft 27 and is rotatably supported in the enlarged portion 23 by a bearing means 30 which, as illustrated, is a roller hearing. The rotor 12 by means of the shaft 27 and the extension 29 is rotatably supported in the cavity of the housing 11.

The rotor 12 has a first bore 31 and a second bore 33 which are preferably cylindrical. The first bore 31 has an axis which extends along the diameter of the surface of the rotor and passes through the center of the rotor and which is perpendicular to the axis of rotation of the rotor 12. The bore 31 has a surface 32 which intersects the surface 26 of the rotor. The second bore 33 intersects the first bore and has an axis which coincides with the axis of rotation of the rotor 12. Adjacent to the first bore 31 are two cylindrical undercuts 35 and 34 whose axis coincides with the axis of rotation.

The surface 26 of the rotor 12 has a sliding fit for engagement with the inner surface 19 of the housing. This engagement provides a good seal between the inner surface 19 of the housing and the rotor 12. To provide additional sealing for the short interval at the time of combustion, sealing means 36 are disposed in grooves 37 formed in the surface 26 about the first bore 31. The grooves 37 are preferably concentric With the axis of the first bore 31. The sealing means 36 may be an expansion type ring which has a fiat spring disposed in the grooves between the sealing means and the bottom of the grooves 37.

The crank means 14 comprising a crank portion 3-8 and a shaft portion 39 is disposed in the rotor and in the housing in the following manner:

As illustrated in FIG. 1, the shaft 39 is disposed in the second bore 33 of the rotor 12 and extends into the bore 21 of the housing means 11. The crank portion 38 is positioned in the first bore 31 of the rotor 12. The shaft 39 of the crank means is rotatably mounted in the rotor 12 by means of a bearing, such as the ball bearing 40, that is inserted in the undercut 34. The crank portion 38 at an end 41 opposite to the shaft 39 is supported in a member 42 which is rotatably supported in the rotor 12 by means of ball bearing 43 mounted in undercut 35. The crank means 14 is adjustably attached to the housing means 11, and for simplification this attachment is shown in FIG. 1 to be made by means of a set screw 44 which is in a threaded bore 45 in the housing means 11. By rotating the crank member in the bore 21 with respect to the housing, the timing of the rotary engine may be accomplished.

The crank member 14 is provided with a lubrication passageway 46 which is in communication with a lubrication or oil inlet means 47 in the housing means 11. The lubrication passageway is in communication with the various bearing surfaces of the rotor and piston. Ring seals 48 and 49 are positioned on shafts 39 and 27 respectively to prevent leakage of the lubricating medium for the cavity of the housing.

The pistons 13 and 13 are disposed in the first bore 31 of the rotor. Each of the pistons has a working surface 50 which preferably conforms with the inner surface 19 of the cavity 20. The surfaces '50 cooperate with the inner surface 19 and the surface 32 of the bore 31 to define chambers 51 and 51. Each of the pistons 13 and 13 has a second surface 52 which conforms to the surface 32 of the first. bore 31 and is in sealing engagement with surface 32 by means of sealing means 53 that may be a standard piston ring disposed in a groove in the surface 52 of the piston. A means 54 rotatably connects the pistons 13 and 13' to the crank portion 3 8 of the crank means 14. As illustrated, the means 54 comprises piston connecting rods. The pistons 13 and 13' are connected to the crank means 14 before the rotor 12 is assembled in the housing means 11. While the pistons 13 and 13' and the connecting means 54 are positioned in bore 31 of the rotor 12, the crank portion 38 is passed through the bore 33 of the rotor 12 and guided through the connecting means 54. The end 41 of the crank portion 38 is then fitted in member 42 and secured against rotation therewith by any suitable means, such as a key and keyway (not illustrated). To facilitate the above assembly, a threaded bore 55, as shown in FIG. 2, is provided in the rotor 12, and is closed by a threaded plug 56 after the completion of the assembly. If the crank portion 38 is too large to pass through the bore 33, the crank portion 38 and shaft 37 may be made separately and assembled together after being placed in the rotor. After the assembly of the parts in the rotor 12 is completed, the housing means 11 is assembled about the rotor.

The piston 13 and 13 have a reciprocal movement in the bore 31 as the rotor 12 revolves about its axis of rotation. Since the crank means 14 is held stationary in the housing, the pistons while reciprocating in the first bore 31 of the rotor are moving about the crank means in an orbit. As the pistons move in the bore 31, the volume of the chambers 51 and 51' will increase and decrease. As illustrated in FIG. 1, the upper piston 13 has a chamber 51 of minimum volume whereas the lower piston 13' has a chamber 51' with a maximum volume.

As illustrated in FIG. 1, the inlet means 24 and the outlet means 25 have associated therewith an inlet valve means 57 and an outlet valve means 5 8, respectively. Inlet valve means 57 is made up of a valve head 59, an inlet valve seat 60 and a stem 61 which is slidably supported in bore 62 of the housing portion 16. Outlet valve means 58 comprises a valve head 63, a valve seat 64 in the housing portion 16 and a stem 65 slidably supported in bore 66 in housing portion 16. The valve means 57 and 58 are actuated by the control means 15. Control means 15 comprises a spur gear 67 mounted on rotor shaft 27. In mesh relationship with the gear 67, are gears 68 and 69. Gear 68 is rotatably supported by means of a bearing 71 on shaft 71 which is secured in a bore in the housing at 72. The gear is prevented from slipping off the shaft 71 by means of a threaded fastener 73. Gear 69 is rotatably supported by means of a bearing 74 on shaft 75 which is secured in a bore at 76 in the housing portion 16. Gear 69 is also prevented from slipping 011 the shaft by means of a threaded fastener 77. Associated with gear 68 is an inlet cam means 78 and associated with gear 69 is an outlet cam means 79. The cam means actuate their respective valve means by a mechanical linkage which comprises the valve stems 61 and 65 which are biased toward the cam means by means of springs 80 and 81, re spectively. As illustrated in FIG. 1 and FIG. 3, the gears 68 and 69 are larger than the gear 67. In the four-cycle engine, the gears '68 and 69 have a 2:1 ratio to gear 67.

Adjacent to and in communication with the inlet means is an ignition means which is illustrated as a spark plug 82. As best illustrated in FIG. 2, the inner surface 19 of the housing means 11 has a groove 83 which is in communication with the inlet means 24 and extends from the inlet means in the direction of rotation of the rotor. A groove 84 extending in the direction of rotation of the rotor is, also, in the surface 19 and is in communication with the outlet means 25.

The housing 11 may be provided with a cooling jacket Which forms a hollow chamber 91 for a cooling medium to be circulated therethr0ugh The operation of the four-cycle internal combustion engine illustrated in FIGS. 1 and 2 is as follows:

Starting in the vertical position, as illustrated in FIG. 2, the piston 13 will have an intake stroke on the first 180 of rotation, followed by a compression stroke on the second 180 of rotation, an ignition or combustion stroke on the third 180 of rotation and finally an exhaust stroke on the fourth 180 of rotation. The second piston, which is indicated at 13', is 180 out of phase with the first piston and lags behind the first piston. Starting in the position illustrated in FIG. 2, the rotor 12 revolves about its axis of rotation, the piston 13 moves away from the surface 19 of the housing means 11 causing the chamber 51 to increase in volume. As the chamber 51 increases in volume, it will intake the fuel mixture as long as the bore 31 is in communication with the arcuate groove 83. During the first rotation of the rotor 12, the outlet or exhaust valve 58 is closed. As the rotation continues, the piston 13 compresses the fuel mixture during the next 180 of rotation and the piston 13' is in an intake stroke similar to that of piston 13. The valve means 57 must be closed before the chamber 51 comes in communication with the inlet means 24 during the compression stroke. As the rotor 12 completes its first revolution, the fuel mixture is ignited by means of the spark plug 82 and the piston 13 will then start its combustion or power stroke. As the piston 13 and its chamber 51 come in contact with the outlet means 25, the outlet valve means 58 is opened to allow the combustion products to be exhausted from the chamber 51 during the final 180 of rotation of the motor. The exhaustion of the combustion products will continue as long as the chamber 51 is in communication with the outlet means 25 by means of the groove 84. At the completion of the exhaust stroke the piston 13 will start the next intake stroke. The cams 78 and 79 are designed to actuate the valve means 57 and 58 to be opened and to be closed at the proper angular displacement of the rotor 12 during the operative cycle. As may be seen from FIG. 2, the angular dimensions of grooves 83 and 84 plus the dimensions of the first bore 31 will dictate at what point in the rotors rotation the valve means should be opened and closed. It should *be noted that the exhaust valve and the inlet valve are both open at the completion of the second revolution since piston 13 is starting a new intake stroke while piston 13 is still in the exhaust stroke. The control means described hereinbefore are mechanically linked to the rotor 12 and are actuated by the angular displacement of the rotor. The rotational force developed by the rotor is transmitted from the shaft 27 which may have a pulley attached thereto.

The two-cycle device, generally indicated by numeral 110 illustrated in FIGS. 4 and 5, has a structure very similar to the embodiment illustrated in FIG. 1.

Briefly, the device 110 has a housing means generally indicated by the numeral 111, a rotor 112 disposed in the housing means 111, pistons 113 and 113' and a crank means generally indicated by numeral 114.

The housing means is made-up of portions 116 and 117 which may be attached or secured together by bolts (not shown). The housing means 111 has an inner surface 119 which is a surface of revolution about an axis and is preferably spherical, the inner surface 119' defines a cavity 120. A cylindrical passageway 121 whose axis coincides with the axis of revolution of the surface 119 passes through the housing. The housing means 111 has an inlet means 124 and an outlet or an exhaust means 125 which are adjacent to each other.

The rotor 112 which has a surface 126 which conforms to the inner surface 119 is disposed in the cavity as is rotor 12 in cavity 20* of the embodiment shown in FIG. 1. The rotor 112 has a shaft 127, which is rotatably supported in the housing 111 in a manner similar to shaft 27, The rotor 112 has a first bore 131 similar to the first bore 31 and a second bore 133 which is similar 6 to the second bore 33 of the embodiment of FIGURE 1. Surrounding the bore 131 are sealing means 136 which are of a similar structure to the sealing means 36 hereinbefore described. The rotors surface 126 conforms to the inner surface 119 in the same manner as surface '26 conforms to the surface 19.

The crank means 114 has a crank portion 138 and a shaft portion 139. The crank portion is disposed in bore 131 in the same manner as crank portion 37 is disposed in bore 31 of rotor 12. The shaft portion 139 is rotatably mounted in bore 133 in the same manner as shaft 39 is supported in bore 33 and is adjusta'bly attached to the housing 111.

The pistons 113 and 113' are disposed in the bore 131 and are connected by means of a connecting rod to the crank portion 138 of the crank means 114 in the same manner that pistons 13 and 13' are connected. Associated with piston 113 is a chamber 151 and associated with piston 113' is a chamber 151.

The major difference in the structure of the two-cycle embodiment from the four-cycle embodiment of FIG. 1 is the design of the inlet and outlet means and the location of an ignition means 182. The ignition means, which is a spark plug, is located diametrically opposite from the inlet and outlet means.

The inlet means 124 comprises a passageway which terminated in an inlet port 186 which is in communication with the cavity 120. The outlet means comprises an outlet or exhaust port 187 which communicates with the cavity 120 and a passageway from the port to an exhaust system, not illustrated. Disposed in the inlet means 124 is a means to prevent back flow in the inlet means, such as a ball check valve 188 and a means to pressurize the fuel mixture which is indicated by numeral 189.

The housing means 111 may be provided with a jacket 190 which forms a hollow chamber 191 which may have a cooling fluid circulated therethrough,

The rotary device 110 operates as a two-cycle engine. As illustratde in FIG. 5, the piston 113 has just completed its compression stroke, and the piston 113' has just completed its power stroke. When the compressed fluid mixture in the chamber 151 is ignited by the ignition means 182, its combustion gases apply a force to the piston which cause the piston and rotor 112 to revolve about the rotors axis of rotation in the direction of arrow 192. When the rotor has completed approximately 180 of rotation, the chamber 151 comes in communication with the exhaust port 187 and then the inlet port 186. The pressurized fuel mixture displaces the combustion gases in chamber 151 by forcing the combustion gases through the outlet port 187. 'During the next 180 of rotation, the piston 113 compresses the fuel mixture and the piston 113' is in its power stroke.

The third embodiment illustrated in FIG. 6 is a fluid motor device generally indicated by numeral 210 and is similar to the four-cycle embodiment illustrated in FIG. 1. The device 120 has a housing means 211 which has disposed therein a rotor 212, pistons 213 and 213 and a crank means 214.

The housing means 211 comprises two housing portions 216 and 217 which may be secured together by fastening means such as bolts 218. The housing means 211 has an inner surface 219 which is a surface of revolution about an axis and is preferably spherical. The inner surface 219 defines a cavity 220. A passageway or bore 221 which is cylindrical and has an axis that coincides with the axis of revolution extends through the housing means 211. The housing means 211 has inlet means 224 and an outlet or exhaust means 225 provided therein.

Disposed in the cavity 220 is a rotor 212 whose surface 226 conforms to the surface of revolution of the inner surface 219. The rotor 212 has a shaft 27 which extends through the bore 221 and is rotatably mounted therein in the same manner in which shaft 27 is mounted in bore 7 21 of the embodiment illustrated in FIG. 1. The rotor 212 has a first bore 231 and a second bore 233 which are the same as bores 31 and 33 of the first embodiment illustrated in FIG. 1. The rotor 212 has additional sealing means 236 which surround the bore 231.

The crank means 214 comprises a crank portion 238 and a shaft 239. The crank portion 238 is disposed in the bore 231 and the shaft extends through the second bore 233 of the rotor 212 and is adjustably secured to the housing means in the same manner in which shaft 39 is secured to housing means 11.

The pistons 213 and 213 are disposed in the first bore 231 and are connected by connection means 254 to the crank portion 238. Associated with the piston 213 is a chamber 251 and associated with the piston 213 is a chamber 251'.

Inlet means 224 and outlet or exhaust means 225 have in communication therewith respectively arcuate grooves (groove 284 is the only one illustrated in FIG. 6). The arcuate grooves are similar to grooves 83 and 84 and are formed in the inner surface 219 of the housing means 211 and extend from their respective inlet and outlet means in the direction of rotation of the rotor 212.

The rotary device of FIG. 6, which has a cross-section substantially the same as that illustrated in FIG. 2, is operated by fluid pressure which may be steam, gas or hydraulic fluid. During the first 180 of rotation, a pressurized fluid entering through port 224 causes the rotor 212 to revolve about the axis of rotation. When the rotor has revolved approximately 180, the chamber 251 will be in communication with the exhaust means 225 and its associated groove 284 and the movement of the piston 213 will force the fluid from the chamber 251 into the exhaust means. During the second 180 of rotation, the piston 213 and the chamber 251 will be acted on by the pressurized fluid and be in a power stroke.

The exhausted fluid may be re-used or disposed of after it leaves through the exhaust means 225.

In the above description of the operation of the three embodiments, the operation has been described as using the device as an engine. It is obvious to a person skilled in the art, that by applying a rotational force to the shaft 227 of the rotor 212 that the device 210 may be used as a compressor or pump.

The rotary devices 10 and 110 with some modification could also be used in a like manner as a compressor or pump.

Although various minor modifications might be suggested by those versed in the art, it should be understood that I wish to employ within the scope of the patent warranted hereon, all such embodiments as reasonably and properly come within the scope of my contribution to the art.

I claim as my invention:

1. A rotary device for converting a source of fluid pressure into rotational motion comprising:

(a) a housing means having an inner surface defining a substantially spherical cavity, a cylindrical passageway having an axis and extending through said housing and said cavity with said axis passing through the center of said cavity, and means including an inlet means and exhaust means for applying a fluid pressure to said cavity and removing the fluid pressure therefrom;

(b) a rotor having an axis of rotation, a substanially spherical surface having a center on said axis of rotation, a shaft extending outwardly along the axis of rotation, and an extension having a passageway extending along said axis of rotation in a'direction opposite to said shaft, said rotor having a bore defining a cylinder which is in communication with the passageway of said extension and having an axis which is perpendicular to the axis of rotation and which extends through said center, said rotor being disposed in said cavity with said extension and shaft being rotatably supported in said passageway of the housing;

(c) a crank means having a crank portion being disposed in said cylinder of said rotor, and a shaft portion being rotatably supported in the passageway of said extension;

(d) a piston being disposed in said cylinder for reciprocation therein and for defining a work chamber therewith, said piston being rotatably connected to said crank portion; and

(e) adjustable securing means disposed on said housing for adjusting the angular position of said crank means in said housing for varying the timing of the maximum piston stroke relative to the angular position of the cylinder to said inlet means, whereby pressure applied to said piston causes said rotor to revolve about the crank and deliver rotational motion to said shaft.

2. A rotary device according to claim 1, wherein said rotor has additional sealing means disposed on said spherical surface about said cylinder.

3. A rotary device according to claim 1, wherein said exhaust means is disposed at an opposite portion of said cavity from said inlet means.

4. A rotary device according to claim 3, wherein said inlet means and said exhaust means each include a port and an arcuate groove in said inner surface of the housing, said groove extending from said port in a direction of the movement of said rotor.

5. A rotary device according to claim 3, in which said means for applying fluid pressure to said cavity further includes an ignition means disposed on said housing adjacent said inlet means and in communication with said cavity for creating said fluid pressure on said piston.

6. A rotary device according to claim 5, wherein a valve means is disposed in each of said inlet and exhaust means, and a control means to open and close said valve means is attached to said housing and is actuated by the movement of said rotor.

7. A rotary device according to claim 6, wherein said inlet means and exhaust means each include a port and an arcuate groove in the inner surface of the housing, said groove extending from said port in the direction of the movement of the rotor.

8. A rotary device according to claim 6, wherein said control means comprises:

(a) a first gear attached to said rotor shaft,

(b) a second gear associated with each valve means and supported by said housing in a mesh relationship with said first gear,

(0) a cam means associated with each of said second gears and adapted to be rotated thereby, and

(d) a biased linkage means between each valve means and its associated cam means, whereby the movement of the rotor causes each of the sec-0nd gears to rotate to move the cam means to cause said linkage to open and close the valve means.

9. A rotary device according to claim 8, wherein the ratio between said first and second gears is 2:1.

10. A rotary device according to claim 1, wherein said exhaust means is disposed adjacent to said inlet means.

11. A rotary device according to claim 10, in which an additional sealing means is disposed in said spherical surface of the rotor about said cylinder.

12. A rotary device according to claim 10, in which means for applying fluid pressure to the gravity includes an ignition means disposed on said housing opposite said inlet and exhaust means and in communication with said cavity for creating said fluid pressure upon said piston.

13. A rotary device according to claim 12, which includes a means to provide a fuel mixture under pressure through said inlet means, said fuel mixture displacing exhaust gases through said exhaust means.

14. In a rotary device for converting fluid pressure to rotational movement, said device having a substantially spherical rotor with a shaft rotatably disposed in a cavity of the housing having inlet and outlet means, a crank means carried by said housing and extending into said rotor, and a piston rotatably connected to said crank means disposed in a cylinder formed in said rotor for reciprocation therein and for rotation about said crank means, the improvement comprising:

adjustable securing means disposed on said housing for varying the angular position of the crank means with respect to the inlet and outlet means of said housing so that the angular position of the cylinder of the rotor at the maximum stroke of the piston can be adjusted with respect to the inlet means.

15. In a rotary device according to claim 14, wherein the outlet means is disposed on an opposite portion of the cavity from said inlet means.

16. In a rotary device according to claim 15, where said inlet and outlet means each include a port and an arcuate groove formed in the surface defining the cavity of the housing, said groove extending from said port in a direction of the movement of said rotor.

References Cited UNITED STATES PATENTS 1,315,897 9/1919 Abel 123-44 3,167,058 1/1965 Czike et a1. 123-44 3,200,797 8/1965 Dillenberg 12344 X FOREIGN PATENTS 31,581 1/1921 Denmark.

ROBERT A. OLEARY, Primary Examiner.

WILLIAM E. WAYNER, Assistant Examiner.

U.S. Cl. X.R. 

